Engine-governing mechanism.



G. H. GIBSON. ENGINE GOVERNING MECHANISNI. 'APPLICATION FILED SEPT-27| 1913.

3 SHEETS-SHEET 1.

Patented Sept. 5,

cru

G. H. GIBSON.

ENGINE GOVERNING IVIECHANISM. APPLICAHON FILED sePLzI. 1913.

Iutcntwitpt. 5, 1916.

3 SHEETS-SHEET 3.

y FAI l lNyENToR "1" A TTORNEY GEORGE E. GIBSON, F MNTCLAIR, NEW JERSEY, ASSIGNOB, T() DE LAVAL STEAM TURBINE CQMPANY, 0F TRENTUN, NEW JERSEY, GORPRATION 0F NEW JERSEY.

ENGNE-GOVERNING MECHANISM.

To all 'whom t mag/concern.:

Be it known that l, GEORGE H. GIBSON, a citizen of the United States of America, residing in Montclair', in the county of Essex and State of New Jersey, have invented a certain new and useful Improvement in Engine-Governing Mechanism, of which the following is a true and exact description, reference being had to the accompanying drawings, which forni a part thereof.

My present invention consists in irnproved governing mechanism, which is well adapted for use in controlling the supply of the motive iiuid to various types of iluid pressure motors such a's steam turbines, and water wheels, and is especially adapted for controlling the supply ot' motive fluid to certain types of steam turbines now in -general use.

The object of the invention is to provide simple and effective mechanism iorthe purpose specified adapted to afford a very definite and effective regulation of the speed of 'the motor to which the mechanism may be applied and capable of insuring, in certain forms, practically absolute uniformity in speed under all loads and in other forms of giving'predetermined and definite speed variations as the load varies.

rlhe various features of novelty which charmzteriz/:e my invention are pointed out with particularity in the claims annexed to and forming a part of thisspecication. l? or a better understanding of the invention, however, and of the 'advantages possessed by it reference should be had to the accompanying drawings and descriptive matter in which have illustrated and described forms in which the invention may be embodied.

OtV thedrawings: Figure 1 is a diagrammatic elevation partly in section illustrating the use of one form of my invention as applied to a steam turbine; 2 isa view taken similarly to Fig. l., illustrating the use'of a second form of my invention as applied to a steam turbine; Fig. 2^" is a view l taken similarly to Fig. 2, showing' a modification of a portion of the apparatus of Fig. 2; Fig. 3 is a partial sectional elevation of a modification of a portion of the valve mechanism employed alike in Figs. .l and 2; Fig. 4 is a partial sectional elevation of another modified form of a valve mechanism which may be employed in. such an arrange- Elpeclcation of Letters latent. Pimp/Inma@ @with 59 jlgjlu l Application filed September 27, 1913. Serial No. 792,084.4

ment as is shown in Figs. 1 and 2; Fig. 5 is a View taken similarly to Fig. l, showing another form of my invention, as applied to steam turbines; Fig. 6 isa sectional elevation illustrating a' modification of a portion of the apparatus shown in Fig. 5; and Fig. is a view taken similarly to Fig. l showing Hstill another form of modification.

lin the drawings, Fig. lis a somewhat conventional illustration of a portion of a multi-stage steam turbine of well known type in which A represents the steam chest, and B, B3 and B3 the nozzles leading therefrom to the first set of moving blades of vanes C, stationary blades orl vanes D being interposed between the first set of moving blades C and a second set of moving blades C. The passage of steam to the steam chest A from the supply pipe A is controlled in theusual manner by a balanced throttle valve E, which, as shown, has its stem E connected to a lever F. The lever F is ulcrumed at F', and is connected at its opposite end to the sliding sleeve G of a centrifugal governor rotating at a velocity proportional to the velocity of rotation of the turbine shaft (not shown) which carries the movable vanes C and C. The

admission of steam to each of the nozzles B', B3 and B3 from the steam chestgflri separately controlled bv a corresponding nozzle valve H', H2 and/H3.

-In so far as above described, the turbine i' and controlling.mechanism shown in Fig. 1 do not diiier from well known types of apparatus in general use. rl`he means aboutto be described. for controlling the operation of the nozzle valves H', H2 and H3, comprise features novel with me, however. As shown, each of the nozzle valves has its stem connected to a piston l, working in a corresponding cylinder J', J2 and J3. Springs K', K3 and K3 interposed between the-inner ends of the cylinders J J3 and J 3 and the pistons l working therein tend to hold the valves H, H3 and H3 open. The outer ends of the cylinders J', J3 and J3 are each connected to a common ,variable pressure systeni L which as shown comprises connected piping and a valve casing M. The system L is connected to a source of pressure Huid such as the compressed air supply tank N through a restricted orifice. O. The valve casing M is provided with an outlet port M which is controlled by the ball valve P.

The ball valve P tends, at all times, to move into, o r remain in a position in which it closes the outlet port M', but is lifted off its seat from time to time as vhereinafter explained by the upper end of the throttle valve stemEf.

With .the apparatus described, it will he apparent that'so long as the pressure within the'variable pressure system L is below the pressurein thecompressed air supply tank N, thereV `will vbe a constant flow' in to the l lvariable pressuresystem tending to bring the rpressure the the pressure 1n i5.

latter :to an equality with .the-tank N. On the other hand, Wheneverfthetvalve'l is lifted ofi' its seat, the subsequent escape of the `pressure fluid from. thevariable system Lf-tends tov reduce the pressure inthelatter to an equality with that ofthe atmosphere. The pres sure Within thevsystem L. may thus be -varied from.v atmospheric pressure up to the presl 'sure inA thetank N." Furthermore, it will be 1s somewhat above the maximum which is to be malntained in the system L, the pressurein the system L will be dependent, solely upon the leakage out of the system, and will be independent of the actual pressure in the tank N.

The pressure in the system' L acting against the outer ends of the pistons I tends to move the latter'into the positions 1111 which the correspondngnozzle valves H',

H? and H3 seat. In the use of my invention -thenozzle valves H',- H? and H3 are mtended to lclose progressively and successively as the pressure. in the syste'mLL rises, opening in the reverse order'asthe pressure falls. This result is obtained with .the mechanism shown in Fig. 1\ in which the pistons I are -all of the same s ize, by making the spring KI3 andthe spring Kz'stronger than the spring K. Vith the particular mechanism shown in Fig. 'l in which the pistons I are engaged by the graduated springs K', K? and'K, the position 'of each piston, prior 'to the closure of the valve connected to it, will depend upon thepressure in the system L, but the parts may be, and preferably are, so proportioned that the ,valve H2 will`n`ot comeclosev enough :to ,its seat to have -an' appreciable.

- throttling effect until after the valve I-I is seated, while similarly thel valve H3 will exert no throttli'ng effect until the valve H2 apparent that if the pressure in the tank N' stronger than the spring K25.

l, a rise in the pressure to which the outer ends of the pistons l are subjected, will re sult first in a gradual closing movement of the nozzle valve ll, and then, if the pressure in the system L continues to rise, in the throttling' follop'ed by the entire closure of the port controlled b v the valve ll', and finally in the tl'irottling and subsequent closure of the port controlled by the valve Upon a diminution in thespeed of the turbine below that whiclrit is desired to maintain, the valveP will be opened by the governor controlled valve stem E so that the consequent reduction in the pressure in the variable system L will bring about a oo rresponding graduated opening movement of the various nozzle valves which will contlnue untll the nozzle valves are all wlde open unless arrested by the return of the turbine speed to its normal value.

Preferably theapparatus shown 1n Fig. 1

`should be so designed and proportioned, that the valve l) is normally cracked, with some leakage continuously taking vplace through' the port M. When the load is steady, this'leakage will obviously be just equal to the inflow through the restricted port O so that .the pressure in the variable pressure'gsystem- L will remain constant and just sufiicient to hold the nozzle valves H,"

H2 and H3 in the positionin which the4 prop er amountof steam is supplied to the f turblne to enable the latter to carry its load lat the. desired speed. Preferably, also, `the capacit ot the, ,variable pressure system `should e large enoughwith -reference to the flow through the ports0 and M when the Ivalve P is moved slightly from its normal positionA that the pressure in the variable pressure system will not instantly become that corresponding to the adjusted position of the valve but will slowly-rise or fall to the last mentioned pressure, which thus depends not only on theparticular position of the valve P but also, to some exteht, on the duration of the time in which it has occupied such position. The movement of the valve I` required to increase or diminish the pressure inthe system L, and thereby decrease or increase the amount of steam supplied to the turbine, blades is very slight, and in practice the parts may-be proportioned to ros make the speedA variation of the turbine incassa in case of failure of the operating means 'for the nozzle valves H', H2 and H3., such as might occur for instance on an accidental reduction of the pressure in the tank N. The Valve'E may, therefore, be entirely dispensed with, or may be operated by some other auto matic emergency mechanism not dependent, for instance, upon the speed governor ein* ployed to control the valve l).

lt will be apparent that the progressively graduated movements of 'the' nozzle valves in response to variations in the pressureof the variable pressure system L may be brought about by other forms ot mechanism than that shown in Fig. 1, and in Fig. 3, l have shown one modification in which the valves H', and H3 are replaced by valves formed by the ends of. plungers P', P2 and l, projecting into the steam chest it through the outer Wall thereof, and carrying at their outer ends corresponding pistons Q', Q2 andr Q3, Working in cylinders JA', JA2 and JA respectively. The outer ends of these cylinders are connected to the system L, as are the cylinders el', J2 and J3 of Fig. l. In the form shown in Fig. 3, the pistons Q', Q2 and Q3, and the piston chambers in which they Work, are oi: progressively decreasing diameters, and the springs KA', KA2 and KA. are of equal strength. It will be apparent Without further explanation that the valves P', P2 and P3 will respond to variable pressures in the system L just as do the valves H', H2 and H" of Fig. l.

ln the modification shown in Fig. 4t, the nozzle valve. HA. shown may be substan tially identical in construction with the valves H', H2 and H3, but the piston LA.

connected to cach valve is provided with a' stem l' which passes through the outer end of the cylinder JP in which the pistony lA Works, and externally thereof, is threaded to receive a hand-wheel l by which the tension of the corresponding spring lili tending to hold the valve open muy be adjustedv as desired. A vent ,llo opening into cylinder JB permits air leaking past the piston lA or steam leaking out of the steam chest along the valve stem to escape to the atmosphere.

Fig. i2 represents a modified type ot my controlling apparatus in which provisions are made 'for varying the speed ot' the turbine in a predetermined manner the load on the turbine` varios. As shown in Fig. 2, the nozzle valves and fluid prcssiixre operating means therefor are identical with the corresponding parts ot' the apparatus shown in Fig. l, but in Fig. 2, the outlet valve P working in the casing lil is not directly responsive to the position of the speed gov-f ernor, but is responsive to the difference trolled valve E. The means employed to obtain this result comprise a differential pressure balancing mechanism consisting of a casing R divided into tivo pressure chambers. R' and R2 by a central diaphragm i', and formed also with a chamber R3, separated from the chamber R2 by a diaphragm r. A third diaphragm r2, preferably of the same diameter as the diameter r', and like it, parallel to and coaxial with the larger diaphragm r, closes an opening formed in the wall of the chamber R. The three diaphragme r, 7" and r2 are connected ytogether at their centers by a stem R4, which has its upper end extended into position to act o'n upper end of the valve stem E in the construction sliown in llig. l. The chambers R' and R2 are connected by conduits R1 and 'R11 to the inlet and outlet compartments respectively, of the casing, of the valve E. The pressures in these compartments correspond, of course, to the pressures in the steam supply pipe A and steam chest A respectively. The chamber R3 is directly connected to the variable pressure system L. lllith this arrangement it will be apparent that the pressure in the steam pipe AO acting upwardly against the diaphragm r2 and downwardly against the larger diaphragm r, tends to depress the valve stem R4, while the pressure of the steam chest A acting upwardly against the diaph agm r and downwardly against the smaller diaphragm if" tends toraise the stem R4. The lifting ac- 100 tion on the stem R4 of the pressure in the v chamber R2 is supplemented by the vaction 'of the'v pressure in the system L against the underside oi the diaphragm r. In practice l prefer to have the pipes R10 and R11 so 105 arranged that the chambers R and R2 will fill with water of condensation, and if the stem R4 is arranged vertically as shown, there may be an appreciable downward thrust on the stem R due to gravity. This 110 may be compensated, or the operation of the apparatus otherwise modified by the spring l 5 acting as shown in Fig. 2^ between the -asing R and a tension adjusting nut R screwed on a threaded portion ot' the stem 115 it". lilith this arrangement shown in Fig. 2, it `will be apparent that as the difference between the pressures in the supply pipe AO and the steam chest A increases, the tendency is to depress the diaphragins and Stem 120 it", thus permitting the valve l to seat and thereby raising the pressure in the system L. rihis rise in pressure transmitted to the chamber lv tends to return the diaphragms and stem R4 to the position in which the 125 valve P is engaged and. lifted from its seat by the stem R4. ln consequence the pressure maintained in the system L, with the apparatus shown in Fig. f2, will rise and fall as the differential between the pressures in the 1w vthe valve P in the same manner as does the chambers R and R2 increases and `minishes. This differential pressure will iii-- crease and diminishfor any given position fof the-governor controlled valve E, as the yvolume of steam passing into the steam chest increases and diminishes, z'. e., as `the load on'the turbinevaries, there being, of course,` a definite relation between the load on the l' chest, it is apparent that with the mecha-` turbine and the volume of steam required to Acarry the load at the speed corresponding tothe vposition of the valve E.

- Since the pressure differential due to the throttling actionnof the valve E decreases lwith the` volume` of the steam passing through the steam chest, while the effect of "an increase in pressure-in the system L is to restrict the flow of steam out of the steam nismshown the maintenance of the balanced v'condition of the apparatus requires that the valve E shouldfapproach and recede froml 'its seat'asthe loaddim-inishes and increases.

soy

, Vdiaphragms 1" vand r2 andthe'size of the The apparatus shown in Fig. 2 will conse- .'quently increase and decrease the turbine Yspeed -as the `load falls and `,rises 4between the no load and full load limits.- This is desirable under 'certain conditions of operation, .particularly where turbine driven elec- Itric generators'are operated inparallel. The

extentl ,to which this speed variation is j 'brought about in Fig. 2 is 'obviously affected bythe ratio between the size of the flexible larger vfiexible diaphragm 1", and any P31" ticula'r regulatingdevice mayV be quickly.

changed byreplacing its diaphragme?" and .r2 b y smaller. or larger diaphragms 'In the modification illustrated in Fig. 5'

the valve casing-M of Fig. 1 is replaced by a valve casing `MA fitted with a chamber M2 to which the piping of the variable pressure is connected. An outlet port M opening from the 4chamber M2 is controlled @by av ball valveP and governor actuated 46 throttle valve stem EB in the same manner va'spthe port ,M5 of the apparatus show'n in Fig.1'is controlled, The casing MAis also 4'formed with a chamber'M* connected to the i chamber M? by a port M3 terminating at its bis lower end in a conicalseat. This port is' controlled by a conical valve PA constantly urged toward the' position in which itcloses lthegport M`3 by a spring P11. The stem P19 s ofthe Valve PA passes through the lower wall of Ithe chamber M4, and isprovided at its lower end with a collar P12. /The collar P12 is adapted to be engaged, and the valve PA thereby moved into its open position on a predetermined decrease in the turbine speedby the arm of the valve stem EB. The chamber M" is directly connected tothe series of compressed air end by the pipe N.`

In the ojieration of this forni of my invention, on a rise in the turbine speed', the governor will depress the valve stem EB. This will permit the valve P to entirely close the outlet port M', and .will depress the valve PA.- Pressure fluid-then passes from the source N through xt fe pipe N chamber M4 and'portM3 intoltlie chamber M2 of the' valve casing MA, thus raising the pressure H3. On a eci'casc in the speed of the turbine, the consquent elevation of the valve stem EB lifts the valve P from its seat and` permits the valve PA to move into position `inwhich it closes the port.N3. This brings about a reduction of the pressure in the variable pressure system, and a corresponding adjustment of thcnozzle valves H',

' H2 rand H3.V lVith this form of my invention it' is possible to build up the pressurein the variable pressure Yiystem more rapidly than this can be `readi y done with the arrangement shown in Fig. l, where the supply of pressure fluid to the system L must all pass through the restricted porto; It will be apparent also that a restricted leakage by the valve PA when in its closed position need not be objectionable, On the j contrary, the restricted leakage of the pressure fluid past this valve will tend to build vup the pressure in the variable system L slowly, just as docs the fiow through the rel'stricted port O, shown inl Fig. l. lVith such a constant leakage of pressure fluidinto the' variable pressure system L, the apparatus may be adjusted so that it will operate est* in variable supply stem L and correspond- `inglynadjusting the nozzle valves H', H2 and would be possible if the ,valve PA were not then opened. nstcad of relying upon leakage past the valve PAA to obtain this mode of operation, I maj/"proceed as shown in Fig. 6. The modification shown in `Fig. 6 differs from the apparatus shown in Fig. 5, inthe addition of a pipe connection N2 containing a restricted `port O, 'and extending between the pressure supply tank N and the valve casing M2. Under some conditions i it may be desirable to have the nozzle valves urged toward-their seats by springs, and ,to

employ the pressure'of the variable pressure system to bring about the opening move. v

ments of? the valves. Due arrangement for accomplishing this is shown 1n Fig. 7, wherein the pistons I of thenozzle valves 11A', HA? and HA3 work in`cyli1iyders JAC/,JCA

and J C3, respectively, which are connected at their lower ends to the vhriable pressure system L. graduated strength act 'between the upper The springs K', K2' and K3 ofi' niet ' l'followers d2 adjustably threaded in the'oujter ends of lltl Aat

dil

the cylinders JU, JGZ and JC. With this arrangement the pressure `in the variable system L should decrease as ,the engine speed increases. 'lllhis resultis'btained by connectingan operating rod M for the valve P to the lever E so that thisrod will rise as the engine speed'decreas'es andtall as the engine speed increases. As shown, rod M is guided at its upper end in a guide M10 earrie'd by the valve casing M and is connected at its lower end to one end of a lever M12 which has its other end connected to the lever E The lever M12 is fulcrumed at lt 13. "W ith the arrangement shown in Fig. 7, an accidental reduction of the pressure in ,the system L will result in the closure of the nozzle valves HA, HAZ and HAS, As shown in Fig. Y, the nozzle valves are balanced valves and it will be understood, of course, that the nozzle valves in all of the forms shown may be balanced valves similar to those shown in Fig. 7'.

While in accordance with the provisions of the statutes l have herein described and illustrated the best form of my invention now known to me, it Will he apparent to those skilled in the art that changes may be made in the form of the apparatus disclosed without departing from the spirit of my invention. i Having now descrihed my invention, what ll claim as new and desire to secure by Letters Patent, is t' l. ln combination, a duid pressure motor having a plurality of motive duid inlets, a separate valve controlling each inlet, fiuid pressure operating means for said valves adapted to open and close said valves successively as the pressure of a pressure fluid supplied to said operating means varies in one direction or the other, and including la variable pressure system having a pressure inlet port and an. exhaust port, a valve con trolling one of said ports, the other of said ports being' more restricted than the valve controlled port when the controlling valve for the latter is in the Wide open position, and means responsive to the speed of the motor ,tor adjusting said valve to progressively vary the pressure of such pressure fluid in one direction or the other on a corresponding variation in the speed of the motor by an amount progressively-increasing during period .in which such variation continues.

2. ln combination, a fluid pressure motor having a plurality of motive fluid inlets, a separate valve controlling each inlet, and operating means for giving said valves sepa rate opening' and closing movements including a' variable pressure system, means for subjecting each valve to a force pro iortionalp to the pressure in said system an tending to give the valve its movement in one direction, means tor sub3ect1ng each valve to an opposing force which becomes equal to the 'said system, a valve regulating the fioW through one of said ports, the other ofsaid ports being more' restricted than the valve controlled port when the controlling valve for the latter is in the Wide open position, and a speed governor for adjusting said valve as the speed of the motor varies, said system being of such capacity and said ports and said valve being so proportioned and arranged that the pressure insaid system `will depend upon the duration as well as the extent of small variations `from the normal of the speed of the motor.

3. ln combination, a fluid pressure motor having a plurality of motive fluid inlets, a separate valve controlling each inlet, a throttle valve .controlling the supply of motive fluid to said inlets, liuid pressure operating means for said inlet controlling valves adapted .to open or close said valves successively as the pressure of a pressure fluid supplied to said operating means varies in one direction or the other, 'means responsive to the speed oi the motor for adjusting said throttle valve, and means governed by said last mentioned means for varying, the pressure in said system on a variation in the speed ol' the motor.

fl. ln combination, a fluid pressure motor havingr a plurality of motive tluid inlets, a separate valve controlling each inlet, a throttle valve controllingthe supply of motive fluid to said inlets, fluid pressure operating means for said inlet controlling valves4 adapted to open or close said valves successively as the pressure fluid supplied to said operating means varies in one direction or the other, means responsive to the speed of the motor for adjusting said throttle valve, and means governed by said last mentioned means for varying the pressure in said system on a speed variation of the motor, less than that required to effect a substantial adjustment of the throttle valve, and hy an amount which increases with the duration of said variation..

in combination, a fluid pressure motor having a plurality of motive fluid inlets, a separate valve controlling each inlet, Huid pressure operating means for said valve adapted to open and close said valves suc- `one, of said ports being restricted, a valve controlling the other port, and means responsive to thevspeed of the motor for adjusting said valve.

6.1In combina-tion, a fluid pressure motor having a plurality of motive Huid inlets, a

separate'valve controlling each inlet, fluid pressureyoperatlng means for said valves l adapted to open and close said valves suceessively as the pressure of pressure fluid supplied to Said operating means varies in .one direction or the other including a variable pressure system having a pressure inlet port and an exhaust port, a valve controllingl one of said ports, the other of said ports being more restricted than the valve controlled port when the controlling valve for the latter is in the wide openposition,

'and means responsive to the load on the motor for adjusting said valve to progressively vary -the pressure of said pressure fluid in one direction or the other'on a cor- `responding variation in the load of the motor by an amount progressively increasing during the period in which such variation continues.

GEORGE H. GIBSON. lVitnesses:

PAUL A. BAUCEL, STAXLEY D. BROWN. 

